JP2018044449A - Oil supply device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To simply configure an oil supply device while avoiding excessive pressure drop of an oil tank.SOLUTION: An oil supply device includes: a main pump 65 for supplying oil to a lubrication section 70 of an engine 12; an oil supply passage 76 that is branched from a main oil passage 69 for connecting the main pump 65 with the lubrication section 70 and is connected to a bearing housing 73 of a turbocharger 19; a catch tank 77 to which oil that has been used for lubrication of the turbocharger 19 is guided; a scavenging pump 66 that is connected to the catch tank 77 via an oil discharge passage 78 to discharge oil from the catch tank 77 to an oil pan 32; and a check valve 81 that is provided in a branch flow passage 80 branched from the oil discharge passage 78 and switched between a communication state and a shut-off state. The check valve 81 is operated to switch to the shut-off state when pressure in the catch tank 77 exceeds reference pressure, and operated to switch to the communication state when the pressure in the catch tank 77 is below the reference pressure.SELECTED DRAWING: Figure 3

Description

  The present invention relates to an oil supply device that supplies oil to a turbocharger of an engine.

  The engine is provided with an oil pump, and oil is supplied from an oil pan to a lubricating portion such as a crankshaft using the oil pump (see Patent Documents 1 and 2). Further, in an engine equipped with a turbocharger, it is necessary not only to supply oil to a lubricating part such as a crankshaft but also to supply lubricating oil to the turbocharger. Furthermore, when the turbocharger is installed below the engine, it is necessary to receive the oil lubricated by the turbocharger in the lower oil tank and return the oil from the oil tank to the oil pan using a scavenge pump. there were.

Japanese Utility Model Publication No. 3-119516 Japanese Utility Model Publication No. 61-183410

  By the way, when an oil tank is installed below the turbocharger, the capacity of the scavenge pump is sufficiently secured so that the oil does not flow back from the oil tank to the turbocharger, that is, the oil does not overflow from the oil tank. This is very important. However, increasing the capacity of the scavenge pump is a factor that excessively depressurizes the inside of the oil tank, and there is a risk that exhaust gas may flow into the oil tank from the gap of the turbine.

  In order to avoid an excessive pressure drop in the oil tank due to the scavenge pump, it is conceivable to connect the oil tank and the rocker cover by a bypass pipe. However, the installation of bypass piping outside the engine not only complicates the oil supply device that supplies oil to the turbocharger, but also requires a countermeasure to prevent blow-by gas leakage. It was. For this reason, it is required to simply configure the oil supply device while avoiding an excessive pressure drop in the oil tank.

  An object of the present invention is to simply configure an oil supply device while avoiding an excessive pressure drop in an oil tank.

  An oil supply apparatus according to the present invention is an oil supply apparatus that supplies oil to a turbocharger of an engine, wherein the oil in the oil pan of the engine is sucked and supplied to a lubricating portion of the engine. And a second supply oil passage that branches off from a first supply oil passage that connects the first oil pump and the lubrication part, and that is connected to an oil supply port formed in the housing of the turbocharger. An oil tank that is connected to the formed oil discharge port and that guides oil that lubricates the turbocharger, and is connected to the oil tank through a discharge oil passage, and discharges oil from the oil tank to the oil pan. A second oil pump and a valve machine that is provided in a branch flow path branched from the discharge oil path and is switched between a cut-off state and a communication state If has the valve mechanism, the pressure in the oil tank is actuated to cut off state when above the reference pressure, the pressure in the oil tank is operated in communication with the case below the reference pressure.

  An oil supply apparatus according to the present invention is an oil supply apparatus that supplies oil to a turbocharger of an engine, wherein the oil in the oil pan of the engine is sucked and supplied to a lubricating portion of the engine. And a second supply oil passage that branches off from a first supply oil passage that connects the first oil pump and the lubrication part, and that is connected to an oil supply port formed in the housing of the turbocharger. An oil tank that is connected to the formed oil discharge port and that guides oil that lubricates the turbocharger, and is connected to the oil tank through a discharge oil passage, and discharges oil from the oil tank to the oil pan. A second oil pump, and a valve mechanism provided at an outside air inlet of the oil tank, which is switched between a shut-off state and a communication state; Has the valve mechanism, the pressure in the oil tank is actuated to cut off state when above the reference pressure, the pressure in the oil tank is operated in communication with the case below the reference pressure.

  According to the present invention, the valve mechanism operates in the shut-off state when the pressure in the oil tank exceeds the reference pressure, and operates in the communication state when the pressure in the oil tank falls below the reference pressure. Thereby, an oil supply apparatus can be simply comprised, avoiding the excessive pressure drop of an oil tank.

It is the schematic which shows an example of the power unit mounted in a vehicle. It is the schematic which shows the engine provided with the oil supply apparatus which is one embodiment of this invention. It is the schematic which shows the structure of the oil supply apparatus which is one embodiment of this invention. (A) is explanatory drawing which shows the interruption | blocking state of a check valve, (b) is explanatory drawing which shows the communication state of a check valve. It is a diagram which shows an example of transition of a catch tank internal pressure. It is the schematic which shows the structure of the oil supply apparatus which is other embodiment of this invention. It is the schematic which shows the structure of the oil supply apparatus which is other embodiment of this invention. (A) is explanatory drawing which shows the interruption | blocking state of a check valve, (b) is explanatory drawing which shows the communication state of a check valve. It is the schematic which shows the structure of the oil supply apparatus which is other embodiment of this invention.

[Embodiment 1]
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a schematic diagram showing an example of a power unit 10 mounted on a vehicle. FIG. 2 is a schematic diagram showing an engine 12 including an oil supply device 11 according to an embodiment (Embodiment 1) of the present invention. The engine 12 shown in FIG. 2 is a horizontally opposed engine, but is not limited to this and may be another type of engine.

  As shown in FIG. 1, the power unit 10 mounted on the vehicle body 13 is arranged vertically from the engine room 14 to the floor tunnel 15. The power unit 10 includes an engine 12 and a transmission 16 connected to the engine 12. A chain cover 17 that covers a timing chain (not shown) is attached to the front of the engine 12. The chain chamber 18 defined by the chain cover 17 is a space communicating with a crank chamber 61 in cylinder blocks 20 and 21 described later. A turbocharger 19 that is a supercharger is installed below the engine 12.

  As shown in FIG. 2, the engine 12 includes a cylinder block 20 constituting one cylinder bank, a cylinder block 21 constituting the other cylinder bank, and a crankshaft 22 supported by the pair of cylinder blocks 20 and 21. ,have. A cylinder bore 23 is formed in the cylinder blocks 20 and 21, and a piston 24 is accommodated in the cylinder bore 23. Further, the crankshaft 22 and the piston 24 are connected via a connecting rod 25.

  Cylinder heads 26 and 27 each having a valve operating mechanism are attached to the respective cylinder blocks 20 and 21. In addition, an intake port 28 and an exhaust port 29 are formed in each cylinder head 26, 27. An intake system 30 is connected to the intake ports 28 of the cylinder heads 26 and 27, and an exhaust system 31 is connected to the exhaust ports 29 of the cylinder heads 26 and 27. Further, an oil pan 32 for storing oil is attached to the lower part of the cylinder blocks 20 and 21.

  The intake system 30 includes an air cleaner box 40, a first intake duct 41, a compressor 42, a second intake duct 43, an intercooler 44, a throttle valve 45, an intake manifold 46, and the like. As indicated by an arrow a1 in FIG. 2, the intake air that has passed through the air cleaner box 40 passes through the first intake duct 41, the compressor 42, the second intake duct 43, the intercooler 44, the throttle valve 45, and the intake manifold 46, It is supplied to the intake port 28 of the cylinder heads 26 and 27.

  The exhaust system 31 includes an exhaust manifold 47, a turbine 48, an exhaust pipe 49, and the like. As indicated by an arrow a <b> 2 in FIG. 2, the exhaust gas discharged from the exhaust port 29 is discharged to the outside through the exhaust manifold 47, the turbine 48 and the exhaust pipe 49. The exhaust pipe 49 is connected to a catalytic converter and a silencer (not shown), and the exhaust gas is discharged to the outside through the catalytic converter and the silencer.

  Further, the intake system 30 is provided with a PCV system 50 that recirculates the blow-by gas to the intake system 30 and reburns it. PCV is an abbreviation for “Positive Crankcase Ventilation”. The PCV system 50 includes a first blow-by pipe 51 that connects the chain cover 17 and the first intake duct 41, and a second blow-by pipe 52 that connects the cylinder block 21 and the intake manifold 46. The second blow-by pipe 52 is provided with a PCV valve 53 that adjusts the flow path area.

  The blow-by gas leaked from the combustion chamber 60 of the engine 12 to the crank chamber 61 flows from the crank chamber 61 to the chain chamber 18 communicating with the crank chamber 61, and then the intake system via the first blow-by pipe 51 or the second blow-by pipe 52. 30. For example, when the throttle opening is small, the internal pressure of the intake manifold 46 is reduced to a negative pressure. Therefore, the blow-by gas passes through the PCV valve 53 and the second blow-by pipe 52 as shown by an arrow b1 in FIG. Supplyed to the intake manifold 46. At this time, part of the air flowing through the first intake duct 41 is supplied to the chain chamber 18 via the first blow-by pipe 51. On the other hand, when the throttle opening is large and the intake air is supercharged by the compressor 42, the internal pressure of the intake manifold 46 rises to a positive pressure, so the PCV valve 53 is closed. At this time, the blow-by gas is supplied to the first intake duct 41 via the first blow-by pipe 51 as indicated by an arrow b2 in FIG. 2 due to the pressure balance between the crank chamber 61 and the first intake duct 41. By using such a PCV system 50, blow-by gas can be supplied toward the combustion chamber 60 of the engine 12, and blow-by gas can be combusted.

  In the above description, the first blow-by pipe 51 is connected to the chain cover 17 and the second blow-by pipe 52 is connected to the cylinder block 21. However, the present invention is not limited to this, and the space through which the blow-by gas flows. You may connect the 1st blow-by piping 51 and the 2nd blow-by piping 52 to the other member which divides. For example, you may connect the 1st blow-by piping 51 and the 2nd blow-by piping 52 to the rocker cover 62 attached to the side part of the engine 12. That is, the locker chamber 63 defined by the rocker cover 62 is a space that communicates with the crank chamber 61 and allows blow-by gas to flow in the same manner as the chain chamber 18 defined by the chain cover 17. Needless to say, the first blow-by pipe 51 may be connected to the cylinder blocks 20 and 21, and the second blow-by pipe 52 may be connected to the chain cover 17.

[Oil supply device]
Next, the configuration of the oil supply device 11 that supplies oil to the turbocharger 19 will be described. FIG. 3 is a schematic diagram showing the configuration of the oil supply apparatus 11 according to one embodiment of the present invention. In addition, the white arrow shown in FIG. 3 has shown the flow direction of the circulating oil.

  As shown in FIG. 3, the rotor 65 a of the main pump (first oil pump) 65 and the rotor 66 a of the scavenge pump (second oil pump) 66 are connected to the crankshaft 22 of the engine 12. Yes. A strainer 68 in the oil pan 32 is connected to the suction port 65i of the main pump 65 via a suction oil passage 67, and a main oil passage (first supply oil passage) is connected to the discharge port 65o of the main pump 65. A lubrication unit 70 such as a crank journal is connected through 69. That is, by driving the main pump 65, the oil in the oil pan 32 is sucked into the main pump 65 and supplied from the main pump 65 toward the lubrication unit 70. Then, the oil that has lubricated the lubrication portion 70 such as a crank journal or a cam journal is returned to the oil pan 32 while falling by its own weight.

  The turbocharger 19 of the engine 12 includes a turbine housing 71 that houses the turbine 48, a compressor housing 72 that houses the compressor 42, and a bearing housing 73 disposed between the housings 71 and 72. Yes. A turbine shaft 75 is rotatably supported on the bearing housing 73 via a bearing 74. An oil supply port 73 i is formed at the upper part of the bearing housing (housing) 73, and an oil discharge port 73 o is formed at the lower part of the bearing housing 73. A supply oil passage (second supply oil passage) 76 branched from the main oil passage 69 is connected to the oil supply port 73 i of the bearing housing 73. A catch tank (oil tank) 77 to which oil that has lubricated the turbocharger 19 is guided is connected to the oil discharge port 73 o of the bearing housing 73.

  A catch tank 77 disposed below the turbocharger 19 is connected to a suction port 66 i of the scavenge pump 66 via a discharge oil passage 78. A discharge oil passage 79 is connected to the discharge port 66 o of the scavenge pump 66, and the end of the discharge oil passage 79 is open to the crank chamber 61. That is, by driving the scavenge pump 66, the oil in the catch tank 77 is sucked into the scavenge pump 66 and discharged from the scavenge pump 66 into the crank chamber 61. Then, the oil discharged into the crank chamber 61 is returned to the oil pan 32 while falling by its own weight.

  By the way, when the catch tank 77 is installed below the turbocharger 19, the scavenge pump 66 is arranged so that the oil does not flow backward from the catch tank 77 to the turbocharger 19, that is, the oil does not overflow from the catch tank 77. It is important to ensure sufficient capacity. Therefore, the capacity of the scavenge pump 66 provided in the oil supply device 11 is designed to be a pump capacity that increases the outflow amount of oil relative to the catch tank 77, that is, a pump capacity that prevents oil from being stored in the catch tank 77. ing.

  Therefore, when the scavenge pump 66 is driven, not only oil but also air is sucked from the catch tank 77, so that the pressure in the catch tank 77 (hereinafter referred to as catch tank internal pressure) decreases. An excessive decrease in the catch tank internal pressure is a factor that causes the exhaust gas to flow into the catch tank 77 through the gap between the turbines 48. For this reason, as will be described below, the oil supply device 11 according to an embodiment of the present invention is configured to suppress an excessive decrease in the catch tank internal pressure.

[Catch tank internal pressure drop suppression structure]
As shown in FIG. 3, a branch flow path 80 is connected to a discharge oil path 78 that connects the catch tank 77 and the scavenge pump 66. A check valve (valve mechanism) 81 that switches between a communication state and a shut-off state is connected to the branch flow path 80 that branches from the discharge oil path 78. The check valve 81, which is a check valve, includes a valve body 82 having an opening 82a that opens in the crank chamber 61, a valve body 83 that is accommodated in the valve body 82 and faces the opening 82a, and toward the opening 82a. And a spring member 84 that urges the valve body 83.

  FIG. 4A is an explanatory diagram showing the shut-off state of the check valve 81, and FIG. 4B is an explanatory diagram showing the communication state of the check valve 81. In addition, the white arrow shown to Fig.4 (a) and (b) has shown the flow direction of the circulating oil. 4 (a) and 4 (b), the space surrounded by the alternate long and short dash line X in which the check valve 81 is accommodated indicates the chain chamber 18 and the crank chamber 61 inside the engine 12. The locker chamber 63 inside the engine 12 is not limited thereto.

  As shown in FIG. 4A, when the catch tank internal pressure exceeds the reference pressure, that is, when the pressure in the discharge oil passage 78 exceeds the reference pressure, the pressure difference acting before and after the valve body 83 is small. Since the thrust for pushing the valve body 83 against the spring force is small, the opening 82a of the valve body 82 is closed by the valve body 83 biased by the spring force. In this way, when the catch tank internal pressure exceeds the reference pressure, the check valve 81 operates in a shut-off state in which the flow from the chain chamber 18 toward the drain oil passage 78 is shut off.

  On the other hand, as shown in FIG. 4B, when the catch tank internal pressure is lower than the reference pressure, that is, when the pressure in the discharge oil passage 78 is lower than the reference pressure, the pressure difference acting before and after the valve element 83 is reduced. Since the thrust for pushing the valve body 83 against the spring force is large, the valve body 83 is pushed and the opening 82a of the valve body 82 is opened. As described above, when the catch tank internal pressure is lower than the reference pressure, the check valve 81 operates in a communication state that allows the flow from the chain chamber 18 toward the discharge oil passage 78.

  As described above, when the check valve 81 is switched to the communication state, blow-by gas (gas) is introduced from the chain chamber 18 into the discharge oil passage 78 as indicated by an arrow α in FIG. A decrease in internal pressure is suppressed. Thereafter, when the catch tank internal pressure rises, as shown in FIG. 4A, the check valve 81 is switched to the shut-off state, and the catch tank internal pressure falls toward the reference pressure.

  FIG. 5 is a diagram showing an example of the transition of the catch tank internal pressure. As shown in FIG. 5, when the engine 12 is started and the main pump 65 and the scavenge pump 66 are driven, the air in the catch tank 77 is sucked by the scavenge pump 66, so that the catch tank internal pressure is the initial atmospheric pressure. It gradually decreases from. When the catch tank internal pressure reaches the reference pressure Ps, the check valve 81 is alternately switched between a communication state and a shut-off state according to the catch tank internal pressure.

  That is, when the catch tank internal pressure is lower than the reference pressure Ps, the check valve 81 is switched to the communication state to increase the catch tank internal pressure, whereas when the catch tank internal pressure is higher than the reference pressure Ps, the check valve 81 is The catch tank internal pressure is reduced by switching to the shut-off state. Thereby, the catch tank internal pressure can be maintained in the vicinity of the reference pressure Ps, and an excessive decrease in the catch tank internal pressure can be suppressed. Here, as shown by the broken line in FIG. 5, when the check valve 81 is not provided, the air in the catch tank 77 is continuously sucked by the scavenge pump 66, so that the internal pressure of the catch tank is greatly reduced. By providing the check valve 81, an excessive decrease in the catch tank internal pressure can be suppressed.

  The reference pressure Ps for switching the operation state of the check valve 81 is set to a pressure at which oil can be discharged from the catch tank 77. That is, when the reference pressure Ps is increased to approach the atmospheric pressure, the amount of oil sucked by the scavenge pump 66 decreases, so that the reference pressure depends on the pump capacity of the scavenge pump 66, the volume of the catch tank 77, and the like. Ps is set appropriately.

  As described so far, by opening and closing the check valve 81 according to the catch tank internal pressure, an excessive decrease in the catch tank internal pressure can be suppressed. Thereby, the inflow of exhaust gas to the catch tank 77 can be prevented and the thrust load of the turbine shaft 75 can be suppressed, so that the load on the turbocharger 19 can be reduced. In addition, in order to suppress an excessive decrease in the catch tank internal pressure, there is no need to provide a bypass pipe for connecting the catch tank 77 and the rocker cover 62 and the oil supply device 11 can be configured easily.

[Embodiment 2]
The oil supply apparatus 90 which is other embodiment of this invention is demonstrated. FIG. 6 is a schematic diagram showing a configuration of an oil supply apparatus 90 according to another embodiment (Embodiment 2) of the present invention. In FIG. 6, the same members as those shown in FIG. 3 are denoted by the same reference numerals and description thereof is omitted.

  As shown in FIG. 6, a branch flow path 80 is connected to a discharge oil path 78 that connects the catch tank 77 and the scavenge pump 66. The branch flow path 80 is connected to an electromagnetic valve (valve mechanism) 91 that is switched between a communication state in which the branch flow path 80 is communicated and a shut-off state in which the branch flow path 80 is blocked. The oil supply device 90 includes a controller 92 that controls the operating state of the electromagnetic valve 91 and a pressure sensor 93 that detects the internal pressure of the catch tank. Then, the controller 92 switches the electromagnetic valve 91 between the communication state and the cutoff state based on the catch tank internal pressure.

  That is, when the catch tank internal pressure exceeds the reference pressure, the controller 92 switches the electromagnetic valve 91 to the cutoff state, and the flow from the chain chamber 18 toward the discharge oil passage 78 is blocked. On the other hand, when the catch tank internal pressure is lower than the reference pressure, the controller 92 switches the electromagnetic valve 91 to the communication state, and the flow from the chain chamber 18 toward the discharge oil passage 78 is allowed.

  In this way, by controlling the electromagnetic valve 91 to open, that is, in a communicating state according to the catch tank internal pressure, the blow-by gas (gas) is introduced from the chain chamber 18 into the discharge oil passage 78 in the same manner as the oil supply device 11 described above. It is possible to suppress an excessive decrease in the catch tank internal pressure. Thereby, the oil supply apparatus 90 can be simply configured while avoiding an excessive pressure drop in the catch tank 77. In the illustrated example, the pressure sensor 93 is provided in the catch tank 77, but the present invention is not limited to this, and the pressure sensor 93 may be provided in the discharge oil passage 78 or the like. The controller 92 that outputs a control signal to the electromagnetic valve 91 is configured by a computer or the like.

[Embodiment 3]
The oil supply apparatus 100 which is other embodiment of this invention is demonstrated. FIG. 7 is a schematic diagram showing a configuration of an oil supply apparatus 100 according to another embodiment (third embodiment) of the present invention. FIG. 8A is an explanatory diagram showing the shut-off state of the check valve 101, and FIG. 8B is an explanatory diagram showing the communication state of the check valve 101. In FIG. 7, the same members as those shown in FIG. 3 are denoted by the same reference numerals, and the description thereof is omitted. Similarly, in FIG. 8, the same members as those shown in FIG. 4 are denoted by the same reference numerals, and the description thereof is omitted.

  As shown in FIG. 7, the catch tank 77 and the scavenge pump 66 are connected to each other via a discharge oil passage 78. In addition, a breather port (outside air inlet) 102 is formed in the upper part of the catch tank 77, and a check valve (valve mechanism) 101 that switches between a communication state and a shut-off state is connected to the breather port 102. The check valve 101, which is a check valve, includes a valve body 103 having an opening 103a that opens to the outside, a valve body 104 that is accommodated in the valve body 103 and faces the opening 103a, and a valve body that faces the opening 103a. And a spring member 105 that biases 104. A breather hose 106 extending upward is attached to the opening 103a of the check valve 101. The upper end 106a of the breather hose 106 is an open end that is opened to the atmosphere.

  As shown in FIG. 8A, when the catch tank internal pressure exceeds the reference pressure, the pressure difference acting before and after the valve body 104 is small, and the thrust for pushing the valve body 104 against the spring force is small. Therefore, the opening 103a of the valve body 103 is closed by the valve body 104 biased by the spring force. In this way, when the catch tank internal pressure exceeds the reference pressure, the check valve 101 operates in a shut-off state that blocks the flow from the breather hose 106 toward the catch tank 77.

  On the other hand, as shown in FIG. 8B, when the catch tank internal pressure is lower than the reference pressure, the pressure difference acting before and after the valve body 104 is large, and the thrust force that pushes the valve body 104 against the spring force is large. Since it is large, the valve body 104 is pushed in and the opening 103a of the valve main body 103 is opened. Thus, when the catch tank internal pressure is lower than the reference pressure, the check valve 101 operates in a communication state that allows a flow from the breather hose 106 toward the catch tank 77.

  As described above, when the check valve 101 is switched to the communication state, the outside air is introduced into the catch tank 77 from the outside via the check valve 101 as indicated by an arrow α in FIG. Is suppressed. Thereafter, when the catch tank internal pressure increases, as shown in FIG. 8A, the check valve 101 is switched to the shut-off state, and the catch tank internal pressure decreases toward the reference pressure.

  Thus, by opening and closing the check valve 101 according to the catch tank internal pressure, the catch tank internal pressure can be converged to the vicinity of the reference pressure. Excessive reduction can be suppressed. Thereby, the oil supply apparatus 100 can be simply configured while avoiding an excessive pressure drop in the catch tank 77.

  Further, by connecting the breather hose 106 to the check valve 101, it is possible to prevent rainwater or the like from entering the check valve 101. Thereby, the check valve 101 can be operated appropriately and the reliability of the oil supply apparatus 100 can be improved. In order to prevent rainwater or the like from entering the check valve 101, it is desirable that the upper end 106a of the breather hose 106 be installed at a height equivalent to the opening of the air cleaner box 40, for example.

[Embodiment 4]
The oil supply apparatus 110 which is other embodiment of this invention is demonstrated. FIG. 9 is a schematic diagram showing the configuration of an oil supply apparatus 110 according to another embodiment (Embodiment 4) of the present invention. In FIG. 9, the same members as those shown in FIGS. 3 and 7 are denoted by the same reference numerals, and the description thereof is omitted.

  As shown in FIG. 9, the breather port 102 of the catch tank 77 is connected to an electromagnetic valve (valve mechanism) 111 that can be switched between a cutoff state and a communication state. By operating the electromagnetic valve 111 in the shut-off state, the breather port 102 can be closed by the electromagnetic valve 111. On the other hand, the breather port 102 can be opened by the electromagnetic valve 111 by operating the electromagnetic valve 111 in a communicating state. Then, the controller 92 that controls the electromagnetic valve 111 switches the electromagnetic valve 111 between the communication state and the cutoff state based on the catch tank internal pressure.

  That is, when the catch tank internal pressure exceeds the reference pressure, the controller 92 switches the electromagnetic valve 111 to the shut-off state, and the flow from the outside toward the catch tank 77 is shut off. On the other hand, when the catch tank internal pressure is lower than the reference pressure, the controller 92 switches the electromagnetic valve 111 to the communication state and allows the flow toward the catch tank 77 from the outside.

  In this way, by controlling the electromagnetic valve 111 to open, that is, in a communicating state in accordance with the catch tank internal pressure, the outside air can be introduced into the catch tank 77 via the electromagnetic valve 111, and the oil supply devices 11 and 90 described above. , 100, an excessive decrease in the catch tank internal pressure can be suppressed. Thereby, the oil supply apparatus 110 can be simply configured while avoiding an excessive pressure drop in the catch tank 77. In the illustrated example, the pressure sensor 93 is provided in the catch tank 77, but the present invention is not limited to this, and the pressure sensor 93 may be provided in the discharge oil passage 78 or the like.

  It goes without saying that the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the scope of the invention. In the illustrated example, the main pump 65 and the scavenge pump 66 are driven by the crankshaft 22. However, the present invention is not limited to this, and the main pump 65 and the scavenge pump 66 may be driven by a camshaft. In the illustrated example, the catch tank 77 is disposed below the oil pan 32. However, the present invention is not limited to this, and the oil pan 32 and the catch tank 77 may be disposed at the same height. The catch tank 77 may be disposed above the oil pan 32. The bearing 74 that supports the turbine shaft 75 may be a ball bearing, a full float bearing, or a semi-float bearing.

11 Oil supply device 12 Engine 18 Chain chamber (inside the engine)
19 Turbocharger 61 Crank chamber (inside the engine)
63 Locker room (inside the engine)
65 Main pump (first oil pump)
66 Scavenge pump (second oil pump)
69 Main oil passage (first supply oil passage)
70 Lubrication part 73 Bearing housing (housing)
73i Oil supply port 73o Oil discharge port 76 Supply oil passage (second supply oil passage)
77 Catch tank (oil tank)
78 Oil discharge path 80 Branch flow path 81 Check valve (valve mechanism)
90 Oil supply device 91 Electromagnetic valve (valve mechanism)
100 Oil supply device 101 Check valve (valve mechanism)
102 breather port (outside air inlet)
110 Oil supply device 111 Electromagnetic valve (valve mechanism)

Claims (6)

An oil supply device for supplying oil to a turbocharger of an engine,
A first oil pump that sucks oil in an oil pan of the engine and supplies oil to a lubricating portion of the engine;
A second supply oil passage branched from a first supply oil passage connecting the first oil pump and the lubrication part, and connected to an oil supply port formed in a housing of the turbocharger;
An oil tank connected to an oil discharge port formed in the housing and guided by oil that lubricates the turbocharger;
A second oil pump connected to the oil tank via a discharge oil passage and discharging oil from the oil tank to the oil pan;
A valve mechanism that is provided in a branch flow path branched from the discharge oil path, and is switched between a shut-off state and a communication state;
Have
The valve mechanism operates in a shut-off state when the pressure in the oil tank exceeds a reference pressure, and operates in a communication state when the pressure in the oil tank is lower than the reference pressure. The oil supply device according to claim 1,
An oil supply device in which gas is introduced from the inside of the engine into the exhaust oil passage through the valve mechanism by operating the valve mechanism in a communicating state. An oil supply device for supplying oil to a turbocharger of an engine,
A first oil pump that sucks oil in an oil pan of the engine and supplies oil to a lubricating portion of the engine;
A second supply oil passage branched from a first supply oil passage connecting the first oil pump and the lubrication part, and connected to an oil supply port formed in a housing of the turbocharger;
An oil tank connected to an oil discharge port formed in the housing and guided by oil that lubricates the turbocharger;
A second oil pump connected to the oil tank via a discharge oil passage and discharging oil from the oil tank to the oil pan;
A valve mechanism that is provided at an outside air inlet of the oil tank and is switched between a shut-off state and a communication state;
Have
The valve mechanism operates in a shut-off state when the pressure in the oil tank exceeds a reference pressure, and operates in a communication state when the pressure in the oil tank is lower than the reference pressure. The oil supply device according to claim 3, wherein
An oil supply apparatus in which outside air is introduced into the oil tank through the valve mechanism by operating the valve mechanism in a communicating state. In the oil supply device according to any one of claims 1 to 4,
The oil supply device, wherein the valve mechanism is a check valve. In the oil supply device according to any one of claims 1 to 4,
The oil supply device, wherein the valve mechanism is an electromagnetic valve.

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